Annular valve

ABSTRACT

A shock absorber includes a first end and a second end that reciprocate relative to one another. The shock absorber includes a gas spring chamber, a damping chamber, and a floating piston. The first side of the floating piston is in fluid communication with the gas spring chamber. The second side of the floating piston is in fluid communication with the damping chamber. The gas in the gas spring chamber applies pressure against the floating piston, which applies pressure to the substantially incompressible fluid in the damping chamber. This pressure transfer may be adequate to minimize or prevent cavitation.

CROSS-REFERENCES TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No.61/869,095 filed Aug. 23, 2013. This application is acontinuation-in-part of U.S. patent application Ser. No. 15/264,808,which was filed on Sep. 14, 2016 and is currently pending, which is acontinuation-in-part of U.S. patent application Ser. No. 14/465,944,which was filed on Aug. 22, 2014 and is now U.S. Pat. No. 9,731,574.These prior applications are hereby incorporated by reference.

STATEMENT REGARDING FEDERALLY-SPONSORED RESEARCH AND DEVELOPMENT

(Not Applicable)

REFERENCE TO AN APPENDIX

(Not Applicable)

BACKGROUND OF THE INVENTION

The present disclosure relates generally to suspension components onvehicles. More particularly, the present disclosure relates to a shockabsorber with a gas spring seal arrangement with reduced friction duringcompression for use on bicycles.

Reducing friction in the compression stroke may improve suspensionresponse and allow for finer control of compression damping. Theseimprovements are of particular interest for off-road cycling, where thecombination of light component weight and suspension compliance ishighly valued.

Shock absorbers that support the weight of the vehicle with compressedgas instead of coil or leaf springs may be attractive for applicationswhere the weight of components must be kept as low as possible.Moreover, gas spring shocks may allow for convenient adjustability ofthe spring rate of the suspension, in some cases by increasing ordecreasing the volume of gas within the shock. Both of these advantageshave made gas spring shock absorbers a popular choice for mountainbikes. However, precisely because the ratio of vehicle-to-passengerweight may be low for bicycles, jounce may be transmitted efficientlyand may be felt keenly by the cyclist. Where terrain is rugged, as inoff-road cycling, it may be desirable for the bicycle's suspension to beas responsive as possible. The difference in responsiveness betweengas-sprung and coil-sprung shocks has proven great enough to limit theuse of gas-sprung shocks in off-road cycling.

Turning to FIGS. 1-4, a conventional gas spring shock may be seen. Aconventional gas spring shock absorber 10 for lightweight vehicles,including bicycles, employs a piston 16 with a gas seal 35 that engagesa cylinder 12. As the seal 35 on the piston 16 moves against the wall ofthe cylinder 12 during compression, the gas trapped in a compressionchamber 22 between the seal 35 and the closed end 32 of the cylinder 12offers progressively greater resistance to compressive movement as asimple function of rising pressure against the sectional area of thepiston 16 and seal 35. Secondarily, this rising gas pressure causes thepiston seal 35 to press with progressively greater force against thecylinder 12. The frictional adhesion of the seal 35 to the cylinder wallmust be overcome before the shock absorber 10 will compress, decreasingresponsiveness.

If an o-ring seal (not shown) is used on the piston of a conventionalgas spring design, the contact area of the seal with the cylindersurface will be relatively large. The area of o-ring contact varies withpressure in the gas spring chamber, since pressure forces the o-ringaxially toward one end of its gland and into conformity with thesquare-cornered sectional profile formed by the gland and cylinder wall.The relatively large contact patch of the o-ring under pressure addssignificantly to the adhesion of the seal to the cylinder.

A u-cup or “X”-section seal (as shown in FIGS. 1-4) will have a smallerarea of contact with the cylinder compared to an o-ring. However, inorder to contain gas pressure reliably, the projecting lip 35 a of sucha seal must be angled toward the cylinder in the direction ofcompression and in the direction of its own movement in relation to thedynamically sealed surface. The angular abutment of the seal lip againstthe cylinder wall 12 drives the pressure of the seal material at thecontact patch to high values during compression. The chisel-action ofthe seal lip creates significant adhesion of the seal material to thecylinder wall, partially offsetting the advantage of a smaller area ofcontact as compared with an o-ring.

The need therefore exists for a gas spring shock absorber with reducedadhesion of the dynamic gas containment seal during the compressionstroke, thereby improving responsiveness.

Further, in some prior embodiments, cavitation may occur in the dampingportion of the shock absorber. The occurrence of cavitation creates aless desirable, rougher ride. Accordingly, the need exists for a shockabsorber where gas pressure may be used to minimize or eliminatecavitation by increasing pressure on the substantially incompressiblefluid in a damping chamber.

BRIEF SUMMARY OF THE INVENTION

In one embodiment, a shock absorber for a vehicle includes a first end,a second end, and a dynamic gas seal. The first end may have an interiorwall and may be adapted to be mounted to one of the frame and a firstwheel of the vehicle. The second end may be reciprocally and slidablymounted to the first end. The second end may be adapted to be mounted tothe other of the frame and the first wheel of the vehicle. Asubstantially gas-tight interior gas spring chamber may be definedbetween the first end and the second end. Gas pressure in the interiorgas spring chamber may bias the first end and the second end away fromone another. The dynamic gas seal may be attached to the first end. Thedynamic gas seal may have at least one lip engaging the second end,thereby creating a substantially gas-tight barrier between the first endand the second end. Movement of the plunger into the interior gas springchamber may reduce the size of the interior gas spring chamber bycompressing gas in the chamber. This decrease in the interior volume ofthe interior gas spring chamber may cause the gas pressure in theinterior gas spring chamber to rise in proportion to the decreasedvolume. Movement of the plunger out from the interior gas spring chambermay increase the size of the interior gas spring chamber and diminishthe pressure on gas in the chamber. This increase in the interior volumeof the interior gas spring chamber may cause the gas pressure in theinterior gas spring chamber to fall in proportion to the increasedvolume. The dynamic gas seal may be the only dynamic seal attachedbetween the first end and the second end and capable of creating asubstantially gas-tight barrier between the first end and the secondend.

The dynamic gas seal may further include a base portion disposed at afree end of the first end. The at least one lip of the dynamic gas sealmay extend both radially and axially away from the base portion. The atleast one lip may also sealingly contact the outer surface of the secondend. Friction between the at least one lip and the second end may belower when the plunger moves into the interior gas spring chamber thanwhen the plunger moves out from the interior gas spring chamber. The atleast one lip may extend axially farther than it does radially.

The vehicle may be a bicycle. The shock absorber may further include ahydraulic damper defined substantially within the second end. Thehydraulic damper may further include a damper chamber within the secondend. Air pressure from the interior gas spring chamber may pressurizefluid within the damper chamber. The hydraulic damper may further dampenmovement of the plunger.

A suspension system may include a first suspension element, a secondsuspension element, and a dynamic seal. The first suspension element mayinclude an interior wall. The second suspension element may be capableof reciprocating relative to the first suspension element and may havean exterior wall that slidingly interfits with and is capable ofreciprocating relative to the first suspension element. The dynamic sealmay have at least one lip and may minimize the escape of gas from withinan interior gas chamber defined between the first suspension element andthe second suspension element. The dynamic seal may be mounted on thefirst suspension element. The dynamic seal may be the only dynamic sealfixed to the first suspension element and capable of creating asubstantially fluid-tight barrier between the first suspension elementand the second suspension element. The interior wall of the firstsuspension element may fit closely with the exterior wall of the secondsuspension element regardless of the reciprocal position of the firstsuspension element relative to the second suspension element. Theinterior wall of the first suspension element may have a consistentcircumference along its length.

The dynamic seal may further include a base portion disposed at a freeend of the first suspension element. The at least one lip of the sealmay extend both radially and axially away from the base portion. The atleast one lip may sealingly contact an exterior wall of the secondsuspension element. Friction between the at least one lip and the secondsuspension element may be lower when the two suspension elements moverelatively in one direction than when the two suspension elements moverelatively in a second direction. The at least one lip may extendaxially farther than it does radially.

The vehicle may be a bicycle. The suspension system may further includea hydraulic damper defined substantially within the second suspensionelement. The hydraulic damper may further include a damper chamberwithin the second suspension element. Air pressure from the interior gaschamber may pressurize fluid within the damper chamber. Fluid pressurefrom the damper chamber may pressurize air from the interior gaschamber.

In one embodiment, a shock absorber for a vehicle includes a first end,a second end, a first piston, a second piston, and a floating piston.The first end may be annular along at least a portion of its length andmay terminate at a first cap. The first end may at least partiallydefine a gas spring chamber containing gas. The second end may beannular along at least a portion of its length and may terminate at asecond cap. The first end and the second end may be configured totelescopically slidingly interfit with one another. The second end mayat least partially define a damping chamber containing a substantiallyincompressible fluid. A first piston may be disposed in fixedrelationship to the second end. Movement of the first piston within thefirst end may affect the gas in the gas spring chamber. A second pistonmay be disposed in fixed relationship to the first end. Movement of thesecond piston within the second end may affect the substantiallyincompressible fluid in the damping chamber. A floating piston may havea first side and a second side. The first side of the floating pistonmay be in fluid communication with the gas in the gas spring chamber andthe second side of the floating piston may be in fluid communicationwith the substantially incompressible fluid in the second chamber. Thevehicle may be a bicycle.

The floating piston may be substantially disc shaped. The floatingpiston may be positioned within the second end.

The floating piston may be substantially annular. The floating pistonmay surround a shaft attached to the first end. The second piston may beattached to the shaft.

The damping chamber may include a first cylindrical chamber, a secondcylindrical chamber and an annular chamber. The damping chamber may beconfigured with a first valve allowing the substantially incompressiblefluid to flow from the cylindrical chamber to the annual chamber duringa compression stroke. The damping chamber may be configured with asecond valve allowing the substantially incompressible fluid to flowfrom the cylindrical chamber to the annual chamber during a reboundstroke. The second valve may be substantially annular. The secondcylindrical chamber may be adjacent the floating piston.

The gas spring chamber may include a first cylindrical chamber, a secondcylindrical chamber, and an annular chamber. The annular chamber mayallow passage of gas between the first cylindrical chamber and thesecond cylindrical chamber. The second cylindrical chamber may beadjacent the floating piston.

The floating piston may be configured to transmit pressure from the gasin the gas spring chamber to the substantially incompressible fluid inthe damping chamber. The pressure from the gas in the gas spring chamberagainst the floating piston may be adequate to minimize cavitation.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

FIG. 1 is a side view of a prior art gas spring for a vehiclesuspension;

FIG. 2 is an end view of the spring of FIG. 1;

FIG. 3 is a cross-sectional view of the spring of FIG. 1 taken alongline 3-3 of FIG. 2;

FIG. 4 is a detailed view of the area shown by a dashed circle in FIG.3;

FIG. 5 is a side view of one embodiment of a vehicle suspensionaccording to the present disclosure;

FIG. 6 is an end view of the suspension of FIG. 5;

FIG. 7 is a cross-sectional view of the suspension of FIG. 5 taken alongline 7-7 of FIG. 6;

FIG. 8 is a detailed view of the area shown by a dashed circle in FIG.7;

FIG. 9 is a side view of another embodiment of a dynamic gas seal;

FIG. 10 is a cross-sectional view of an alternative embodiment of thesuspension;

FIG. 11 is a cross-sectional view of another alternative embodiment ofthe suspension; and

FIG. 12 is a cross-sectional view of the embodiment of FIG. 11 taken online 12-12 of FIG. 11.

In describing the preferred embodiment of the invention which isillustrated in the drawings, specific terminology will be resorted tofor the sake of clarity. However, it is not intended that the inventionbe limited to the specific term so selected and it is to be understoodthat each specific term includes all technical equivalents which operatein a similar manner to accomplish a similar purpose. For example, theword connected or terms similar thereto are often used. They are notlimited to direct connection, but include connection through otherelements where such connection is recognized as being equivalent bythose skilled in the art.

DETAILED DESCRIPTION OF THE INVENTION

In this detailed description, various terms relating to direction may beused. The elements discussed herein relate to a bicycle. Because, in itsoperable position, a bicycle is oriented generally vertically, i.e.,perpendicular to the ground, the direction terms refer to the positionof an element relative to gravity when the bicycle is in its operableposition. Accordingly, for example, the term “downwardly” refers to thedirection towards the ground when the bicycle is in its operableposition, and the term “forwardly” relates to a direction towards afront wheel of the bicycle when it is in its operable position. Further,the terms “inboard” and “outboard” may be used. The term “inboard”describes a position between one item and a vertical plane substantiallybisecting the bicycle. The term “outboard” describes a position of anobject further from the vertical centerplane of the bicycle. Inaddition, the terms “bicycle” and “bike” are used hereininterchangeably. A person having ordinary skill in the art willunderstand that if something is referred to as one, it can refer to theother.

In the present disclosure, the suspension structure may be described asit relates to a bicycle. However, the suspension structure described inthe present embodiments may instead be applied to other vehicles. Thepresent suspension structure may be used with vehicles having adifferent number of wheels, for example. The suspension structure may beused in connection with a motorized vehicle.

The present embodiments may reduce seal adhesion in a gas spring shockabsorber. In some embodiments, the gas-compressing element may be aplunger or large-diameter blind rod slidingly engaging a seal containedin the cylinder. The lip of the u-cup that forms the dynamic gascontainment seal may be angled toward the gas spring chamber so thatrising pressure pushes the seal progressively harder against the surfaceof the plunger, but because the plunger surface moves compressively inthe same direction in which the lip of the seal is biased, there is noaccompanying chisel-action of the seal lip to compound the pressure atthe contact patch and contribute undesirably to adhesion. By eliminatinga structural contributor to seal adhesion (“stiction”), the presentinvention may be more responsive to bumps than is a conventional gasspring shock absorber.

Turning now to FIG. 5, a shock absorber or suspension system 110 may beseen. The suspension system 110 may have a first housing member, portionor end 112 and a second housing member, portion or end 114. A first eyehole 124 may extend from a closed end 140 of the first portion 112. Asecond eye hole 126 may extend from a closed end 142 of the secondportion 114. In some vehicles, one of the first eye hole 124 and thesecond eye hole 126 may be directly or indirectly secured to a vehicleframe (not shown) in conventional fashion. The other of the first eyehole 124 and the second eye hole 126 may be secured directly orindirectly to a vehicle wheel (not shown) in conventional fashion.

As may be seen most clearly in FIG. 7, the suspension system may includetwo components. The first is a conventional hydraulic damping portion144 and an air spring portion 146. While various components areillustrated of the hydraulic damping portion 144, these components arerelatively conventional. Many other configurations of hydraulic dampingmay be substituted therefor by a designer or other person havingordinary skill in the art. Accordingly, these components are not furtherdescribed in detail.

Turning now to the air spring portion 146, it may be seen that the firstportion 112 may include an inner wall 148 and the second portion 114 mayinclude an outer wall 158. The inner wall 148 and the outer wall 158 maybe configured to be of similar shape and size, while allowing the innerwall 148 and the outer wall 158 to slidingly interfit with one anotherto allow the first portion 112 and the second portion 114 to reciprocaterelative to one another.

The first portion 112 may terminate in a free end 162. The free end 162may be open to allow the insertion of the second portion 114. The secondportion 114 may terminate in a plunger or other closed end structure164. An interior gas spring chamber 122 may be defined between the firstportion 112 and the second portion 114. The gas spring chamber 122 maybe defined between the inner wall 148 of the first portion 112 and theplunger 164. The gas spring chamber 122 may be filled with any desirablegas through a conventional port to a desired pressure level. Thepressure in the gas spring chamber 122 may desirably be selected to besufficient to bias the plunger 164 away from the closed end 140 of thefirst end 112, thereby biasing the first end 112 and second end 114relatively away from one another.

When the wheel of the vehicle encounters an obstacle, the impact may beat least partially absorbed by the suspension element 110. The impactmay cause the plunger 164 to move toward the closed end 140 of the firstportion 112. This movement may reduce the size of the gas chamber 122,thereby causing the gas in the gas chamber 122 to compress andincreasing the gas pressure in the chamber 122 in proportion to thereduction in the interior volume of the chamber 122 caused by theplunger. Upon removal of the impact force, the gas pressure force mayexceed the impact force and move the plunger 164 away from the closedend 140 of the first portion 112. This movement may cause an increase inthe size of the gas chamber 122 and a decrease in the gas pressure inthe chamber 122 in proportion to the increase in the interior volume ofthe housing by the plunger 164.

In many embodiments, it is desirable for there to be only one gas springchamber. In contrast to the prior art embodiment shown in FIGS. 1-4, nosupplemental chamber is used between the plunger 16 and the cap 30. Inthe prior art embodiment, there is included an outward-facing flange 31on the second portion 14 and an inward-facing flange 33 on the firstportion 12. This set of flanges cooperated to create a first gascylinder 22 and a second gas cylinder 23. The second gas cylinder 23 isoften used to oppose extension of the first and second portions relativeto one another. It is also noted that in such a design, there are twodynamic seals used between the first portion 12 and the second portion14. One dynamic seal is attached to the first portion 12 on itsinward-facing flange 33 and contacts the outer surface of the secondportion 14. A second dynamic seal is attached to the second portion 14on its outward facing flange 31 and contacts the inner surface of thefirst portion 12.

In the present embodiment, instead of including cooperating flanges,there may be no need for a secondary gas cylinder. The outercircumference of the second portion 114 may be substantially the samealong its length. Similarly, the inner circumference of the firstportion 112 may be substantially the same along its length. This closefit may allow for a minimum of binding between the parts.

Other features of the device are also conventional and are illustrated.For example, in FIG. 7, there is illustrated a structure 700 that allowsfor adjustment of air pressure within the air chamber 122. Thisstructure 700 may incorporate a variety of static seals that may serveto contain air pressure within the interior gas chamber 122. Similarly,there is illustrated a structure 702 that allows for adjustment ofhydraulic pressure within the damper chamber 704. This structure 702 mayalso incorporate a variety of static seals that may serve to contain airpressure within the damper chamber 704.

Turning now to FIG. 8, a more detailed view may be seen of the seal 150b that is attached and extends between the first portion 112 and thesecond portion 114. The seal 150 b may include a base portion 160 a thatmay be inserted into or otherwise secured to a finger 160 disposed at oradjacent the free end 162 of the first end 112. The seal 150 b mayfurther include at least one lip portion 166 that extends both axially(along the axis 168 of the suspension system 110) and radially (towardsthe axis 168 of the suspension system 110). In some embodiments, it maybe desirable for the at least one lip portion 166 to extend axially agreater distance than it extends radially. The seal 150 b, and in manyembodiments, the lip portion 166, may be configured to sealingly engagethe outer surface 158 of the second portion 114. The use of such a sealmay minimize the escape of gas from the gas spring chamber 122. The lipportion 166 may have a thickness 802 and the base 160 a may have athickness 804. The thickness 802 of the lip portion 166 may be less thanabout half of the thickness 804 of the base 160 a. The lip portion 166may have a length 806, and the base 160 a may have a length 810. Thelength 806 of the lip portion 166 may be less than about half of thelength 810 of the base 160 a. In many embodiments, it may be desirablefor a free end 812 of the lip portion 166 to engage the second housingmember 114. In many embodiments, the lip portion 166 may be axiallydeformable to allow axial movement, particularly of the free end 812towards and away from the axis 168.

An alternative embodiment of the seal may be seen in FIG. 9. FIG. 9illustrates a seal 950 b that has a base portion 960 a. The seal 950 balso includes a first lip 966 and a second lip 967. As may be seen inFIG. 9, the first lip 966 and the second lip 967 may be of similar sizeand shape and may project from the base portion at substantially thesame angle. However, a designer may choose to vary the thickness andangle of protrusion of each of the lips 966, 967 away from the baseportion 960 a. The lips may each extend both radially and axially fromthe base portion and may extend the same or different lengths radiallyand axially. Further, any number of lips may be used instead of thoseillustrated in FIGS. 5-10. The embodiments shown are merely exemplary.

The configuration of the seal 150 b in FIG. 8 may allow for improvedrelative reciprocation of the first portion 112 and the second portion114. When the first portion 112 moves towards the second portion 114(reducing the size of the gas spring chamber 122), the lip portion maydeform in an inward direction relative to the axis 168 (away from thesecond portion 114) and minimize the surface area of the seal thatcontacts the second portion 114. This inward deformation may cause theseal to take a chisel shape that may allow for adequate containment ofthe gas. In the orientation shown in FIG. 8, the compression stroke willinvolve the first end or portion 112 moving towards the left, towardsthe second end or portion 114. As may be apparent, when the first end112 moves towards the second end, the lip portion 166 may deformoutwardly and partially into the cavity 170 within the seal 150 b. Thisdeformation may minimize contact and friction between the seal 150 b andthe outer surface 158 of the second end 114. This deformation may allowthe compression stroke to occur with a minimum of friction between theseal 150 b and the second end 114.

However, during the rebound stroke, the seal 150 b has an oppositeeffect. When the first end 112 moves away from the second end 114(towards the right in FIG. 8), the lip portion 166 may move inwardly(towards the axis 168). This inward movement may create an increaseddrag or friction between the seal 150 b and the second end 114. Thisfriction may prevent or minimize the effects of premature rebound of theshock absorber.

The precise design of the seal 150 b and its attachment to the first end112 may be modified by a person having ordinary skill in the art. Whilethe seal 150 b is attached to a finger 160 adjacent a dust guard (wipingseal) 153 at the free end 162 of the first end 112, this structure maybe modified. For example, the finger 160 may be configured differently.The finger 160 may be thicker or thinner than that shown. It may bepositioned at a different angle relative to the axis 168. It may becurved or have any other desirable profile.

The seal 150 b may be secured adjacent the free end 162 in a number ofdifferent ways. The seal 150 b may be affixed to the first end 112 by anadhesive. Alternatively, it may be positioned within a cavity, such asthe cavity 172, without any adhesive. Alternatively, it may be securedwith a fastener. Other methods and structures for attaching or securingthe seal 150 b in or to the first end 112 are within the capabilities ofa person having ordinary skill in the art.

The relative size and shape of the seal 150 b and the apparatus as awhole may also be modified by a person having ordinary skill in the art.A designer will be able to modify the size and shape of the seal 150 b,along with the extents of its axial and radial extensions in order toproduce a desired friction. Further, the seal 150 b may be made from avariety of materials capable of substantially producing a seal toenclose air within the shock absorber 110. A designer is able to selectan appropriate material to provide an appropriate durability, adhesion,and friction, based on the designer's criteria. In some embodiments, thematerial may be selected from nitrile, polyurethane, and fluorocarbon.In some embodiments, the material of the seal may have a Shore Ahardness between about 60 and about 90.

In many embodiments, the dynamic seal 150 b may be the only dynamic sealattached to the first end 112 capable of creating a substantiallyfluid-tight barrier between the first end 112 and the second end 114.Other seals may, of course be present and may be attached to the firstend 112. For example, the dust wiping seal 153 may also be securedadjacent a free end 162 of the first end 112. However, the dust wipingseal 153 is not capable of creating a substantially fluid-tight sealbetween the first end 112 and the second end 114, due to its orientationand purpose. As also noted above, there may be static seals elsewhere inthe design that may be attached to the first end 112 and that maycontribute to the creation of a substantially gas-tight chamber 122. Aswill be described below in connection with FIG. 10, there may be someembodiments where a passageway is created through or around the plunger164 to create an interaction between the interior gas spring chamber 122and the damper chamber 704. In such embodiments, additional dynamicseals may be incorporated into the design. However, these dynamic sealsare not attached directly to the first end 112 and do not serve tocreate a substantially gas-tight barrier directly between the first end112 and the second end 114. Accordingly, such other seals are attacheddifferently and may serve very different purposes than that of thedynamic gas seal 150 b.

The remaining features of the design may also be modified as a designerwishes. The present embodiments may be used with a variety of hydraulicdampers. The design shown may be modified in a variety of ways known toa designer of ordinary skill to achieve the desired dampingcharacteristics.

For example, an alternative embodiment is shown in FIG. 10. In thealternative shock absorber or suspension system 1000 illustrated in FIG.10, there is a first end 1002 and a second end 1004. The dynamic sealingstructures 1005 and overall configuration are substantially the same asthose described above in connection with FIGS. 5-8 and this descriptionwill not be repeated here. However, FIG. 10 illustrates a furtherfeature that may be incorporated.

FIG. 10 illustrates an interior gas spring chamber 1006 definedsubstantially within the first end 1002 and further bounded by a plunger1008. The suspension system 1000 further includes a hydraulic dampingchamber 1010 defined substantially within the second end 1004 andfurther bounded by a piston 1012. In some embodiments, it may bedesirable to incorporate a secondary gas chamber 1014 adjacent thehydraulic damping chamber 1010 and fluidly connected to the interior gasspring chamber 1006 by a gas passageway 1016. A floating ring 1020 maybe positioned between the secondary gas chamber 1014 and the hydraulicdamping chamber 1010 to separate the gas and the hydraulic fluid and toallow force to be mutually created between the gas and the hydraulicfluid. In many embodiments, it may be desirable to incorporate one ormore seals 1018 on the floating ring within the second end 1004 tominimize interaction between the gas and the hydraulic fluid. When avehicle, such as a bicycle, encounters an obstacle, the first end 1002and the second end 1004 move relatively toward one another, i.e., thefree end 1024 of the first end 1002 moves left as illustrated and thefree end 1026 of the second end 1004 moves right as illustrated. Thismovement causes the plunger 1008 to compress the gas in the interior gaschamber 1006 and the plunger 1012 to compress the fluid within thedamper chamber 1010. Upon such movement, the gas under pressure flowsinto the interaction chamber 1014 and presses on a first side 1022 ofthe floating ring 1020. Similarly, pressure from the hydraulic fluid inthe damper chamber 1010 presses on a second and opposite side 1023 ofthe floating ring 1020. This pressure from each side serves to dampmovement of the piston and the plunger. Accordingly, fluid pressure fromthe damper chamber 1010 may damp movement of the plunger 1008 into thegas chamber 1006 and gas pressure from the gas chamber 1006 may dampmovement of the piston 1012 into the damper chamber 1010. The inclusionof such an interaction chamber may, therefore, allow for better tuningof compression and rebound of the shock absorber 1000.

FIGS. 10 and 11 may be compared to demonstrate different ways a shockabsorber can be configured to permit a beneficial interaction between agas spring chamber and a damping chamber. In both embodiments, gas fromthe gas spring chamber is in fluid communication or contact with oneside of a floating piston. Substantially incompressible fluid from thedamping chamber is in fluid communication or contact with an oppositeside of the floating piston. In this manner, pressure from the gas inthe gas spring chamber can be used to pressurize the substantiallyincompressible fluid in the damping chamber, thereby, among otherthings, minimizing or preventing vacuum bubbles within the substantiallyincompressible fluid.

As previously described, the shock absorber 1000 in the embodiment ofFIG. 10 may include a first end 1002 and a second end 1004. The firstend 1002 and the second end 1004 are configured to slidingly interfitwith or be telescopic with one another. The first end 1002 may beannular along at least a portion of its length and may terminate in afirst cap. The first cap may include an eye 1024 that may be used tosecure the first end 1002 to a vehicle (not shown). The first end 1002may at least partially define a positive gas spring chamber 1006. Thegas spring chamber 1006 may be filled with gas to a conventionalpressure in a conventional manner. The second end 1004 may be annularalong at least a portion of its length and may terminate in a secondcap. The second cap may include an eye 1026 that may be used to securethe second end 1004 to a different portion of a vehicle (not shown). Thesecond end 1004 may at least partially define a damping chamber 1010.Upon compression, a first piston 1008 secured or otherwise disposed in afixed relationship to the second end 1004 may move towards the first end1002. This movement of the first piston 1008 may affect the gas in thegas spring chamber 1006. In many embodiments, the movement of the firstpiston 1008 may compress the gas in the positive gas spring chamber1006. Simultaneously, a second piston 1012 secured or otherwise disposedin a fixed relationship to the first end 1002 may move towards thesecond end 1004. This movement of the second piston 1012 towards orwithin the second end 1004 may affect the substantially incompressiblefluid in the damping chamber 1010. In many embodiments, the movement ofthe second piston 1012 may create a displacement of oil or otherincompressible fluid in the damping chamber 1010. This oil displacementis done in a conventional manner with valving in the piston or in thesecond end 1004 to allow the substantially incompressible fluid to movefrom one damping chamber to the other.

The shock absorber 1000 may further include a floating ring or piston1020 having a first side 1022 and a second side 1023. Gas in fluidcommunication with the positive gas spring chamber 1006 may be capableof contacting the first side 1022 of the floating piston 1020.Substantially incompressible fluid in fluid communication with thedamping chamber 1010 may be capable of contacting the second side 1023of the floating piston 1020. The floating piston 1020 may be responsiveto the relative pressures of the gas in the positive gas spring chamber1006 and of the substantially incompressible fluid in the dampingchamber 1010 and may be permitted to move to maintain the pressuressubstantially in equilibrium.

As shown in FIG. 10, the air spring chamber 1006 may include a firstsubstantially cylindrical chamber 1050, a secondary chamber orinteraction chamber or second substantially cylindrical gas chamber1014, and an annular chamber 1016. Additional chambers or passagewaysmay be included in fluid communication between these chambers, ifdesired or deemed appropriate by a person having ordinary skill in theart, such as the passageways 1052. Gas within the gas spring chamber1006 is permitted to move without restriction between the firstsubstantially cylindrical chamber 1050, the second substantiallycylindrical gas chamber 1014, and the annular chamber 1016. In manyembodiments, such as the illustrated embodiment, gas may flow freelybetween the chambers and passageways. In other embodiments, one or morevalves may be incorporated within the gas spring chamber 1006. Gaswithin the second cylindrical gas chamber 1014 may be in contact withone side of the floating piston 1020, such as the first side 1022 asillustrated in this embodiment.

During a compression stroke, the first end 1002 and the second end 1004may telescopically slide towards one another. The first piston 1008 maymove into the gas spring chamber 1006. This motion of the first piston1008 may cause gas to move between the sub-chambers of the gas springchamber 1006 and may also increase the pressure in the gas springchamber 1006. This fluid movement and pressure increase may increase thepressure of the gas in the second cylindrical chamber 1014 against thefirst side 1022 of the floating piston 1020. At the same time, thesecond piston 1012 may move into the damping chamber 1010. The movementof the second piston 1012 may cause the opening of a valve within thesecond piston 1012 to create a damping of the movement of the shockabsorber 1000. Such valving and damping is well known by persons havingordinary skill in the art and is not further described in detail. Oneembodiment of relevant valving is shown in FIG. 10 and identified as1054. The pressure applied by the gas in the gas spring chamber 1006 tothe floating piston 1020 may minimize or prevent vacuum bubbles fromforming (i.e., cavitation) in the fluid of one or more damping chambers1010 as the second piston 1012 moves during extension and compression ofthe shock absorber 1000. The prevention of vacuum bubbles in the dampingfluid may be desirable to maintain a substantially consistent dampingforce, as is known in the art. In addition, varying the gas pressurewithin the gas chamber 1006 may vary the tension on the seal 1018 of thefloating piston 1020 that may be overcome in order for the floatingpiston 1020 to move and permit the shock absorber 1000 to compress. Inthis manner, gas pressure from the gas spring chamber 1006 may be usedto affect the damping of the shock movement.

A person having ordinary skill in the art and a related user can easilyadjust the shock absorbing and damping characteristics of the shockabsorber 1000 merely by adjusting the air pressure within the gas springchamber 1006. There is an interrelationship between the pressure in thegas spring chamber 1006 and the pressure in the damping chamber 1010through the equalizing effect and movement of the floating piston 1020(as will be described in greater detail below). Accordingly, by addingor removing gas from the gas spring chamber 1006 alone, the dampingcharacteristics will also change as described above. Thisinterrelationship, particularly by allowing adjustment of the pressureof the gas in the gas spring chamber 1006 through a conventionalSchrader valve open to the gas spring chamber 1006, may allow a user toeasily adjust these characteristics.

A similar configuration may be seen in FIGS. 11 and 12. The shockabsorber 1100 in the embodiment of FIG. 11 may include a first end 1102and a second end 1104. The first end 1102 and the second end 1104 may beconfigured to slidingly interfit with or be telescopic with one another.The first end 1102 may be annular along at least a portion of its lengthand may terminate in a first cap. The first cap may include an eye 1124that may be used to secure the first end 1102 to a vehicle (not shown).The first end 1102 may at least partially define a positive gas springchamber 1106. The gas spring chamber 1106 may be filled with gas to aconventional pressure in a conventional manner. The second end 1104 maybe annular along at least a portion of its length and may terminate in asecond cap. The second cap may include an eye 1126 that may be used tosecure the second end 1104 to a different portion of a vehicle (notshown). The second end 1104 may at least partially define a dampingchamber 1110. Upon compression, a first piston 1108 secured or otherwisedisposed in a fixed relationship to the second end 1104 may move towardsthe first end 1102. This movement of the first piston 1108 may affectthe gas in the gas spring chamber 1106. In many embodiments, themovement of the first piston 1108 may compress the gas in the positivegas spring chamber 1106. Simultaneously, a second piston 1112 secured orotherwise disposed in a fixed relationship to the first end 1102 maymove towards the second end 1104. This movement of the second piston1112 towards or within the second end 1104 may affect the substantiallyincompressible fluid in the damping chamber 1110. In many embodiments,the movement of the second piston 1112 may create a displacement of oilor other incompressible fluid in the damping chamber 1110. This oildisplacement may be done in a conventional manner with valving in thepiston or in the second end 1104 to allow the substantiallyincompressible fluid to move from one damping chamber to the other.

The shock absorber 1100 may further include a floating piston 1120having a first side 1122 and a second side 1123. The floating piston1120 may be annular and may surround a portion of a shaft 1121. Thesecond piston 1112 may be secured to the shaft 1121. The shaft 1121 mayalso be attached to the first end 1102. Gas in fluid communication withthe positive gas spring chamber 1106 may be capable of contacting thefirst side 1122 of the floating piston 1120. Substantiallyincompressible fluid in fluid communication with the damping chamber1110 may be capable of contacting the second side 1123 of the floatingpiston 1120. The floating piston 1120 may be responsive to the relativepressures of the gas in the positive gas spring chamber 1106 and of thesubstantially incompressible fluid in the damping chamber 1110 and maybe permitted to move to maintain the pressures substantially inequilibrium.

As shown in FIG. 11, the damping chamber 1110 may include a firstcylindrical chamber 1160, a second cylindrical chamber 1162, a thirdcylindrical chamber 1164 and an annular chamber 1166. The dampingchamber 1110 may include a first port 1186 and a first valve 1168 and asecond valve 1194 that may govern fluid flow between the firstcylindrical chamber 1160 and the annular chamber 1166, as best shown inFIG. 12. This first port 1186 may permit the substantiallyincompressible fluid to flow in either direction between the firstcylindrical chamber 1160 and the annular chamber 1166. The first valve1168 may permit fluid to flow from the first cylindrical chamber 1160,through the first port 1186 and into the annular chamber 1166 whenpressure or force from the incompressible fluid in the first cylindricalchamber 1160 exceeds any necessary force threshold within the valve1168. In some embodiments, features of the valve 1168 may extend beyondthe exterior surface 1190 of the second end 1104 and may be manipulableby the user via a knob or other structure 1180 to adjust the pressure atwhich the substantially incompressible fluid may flow through the firstport 1186 from the first cylindrical chamber 1160 to the annular chamber1166. In some available positions of the adjustment structure 1180, thenecessary pressure to open the first valve 1168 may be, or may approach,zero. In some embodiments, the valve 1168 may permit fluid to freelyflow through the first port 1186 from the annular chamber 1166 into thefirst cylindrical chamber 1160, so that the valve may restrict flow inonly one direction. In some embodiments, the valve 1168 may be acontrollable plain orifice valve in the direction from the firstcylindrical chamber 1160 to the annular chamber 1166 and a sprung valvein the direction from the annular chamber 1166 to the first cylindricalchamber 1160.

The second valve 1194 may also permit fluid to flow from the firstcylindrical chamber, through the first port 1186, and into the annularchamber 1166. In some embodiments, the second valve 1168 may permitfluid to freely flow through the first port 1186 from the annularchamber 1166 into the first cylindrical chamber 1160. In someembodiments, the second valve 1194 may permit the substantiallyincompressible fluid to flow from the annular chamber 1166, through thefirst port 1186 and into the first cylindrical chamber 1160 whenpressure or force from the incompressible fluid in the annular chamber1166 exceeds any necessary force threshold within the second valve 1194.In some embodiments, features of the second valve 1194 may extend beyondthe exterior surface 1190 of the second end 1104 and may be manipulableby the user via a knob or other structure 1196 to adjust the pressure atwhich the substantially incompressible fluid may flow through the firstport 1186 from the annular chamber 1166 to the first cylindrical chamber1160. In some available positions of the adjustment structure 1196, thenecessary pressure to open the second valve 1194 may be, or mayapproach, zero. Using this structure, the second valve 1194 may restrictflow in only one direction. In some embodiments, the valve 1194 may be acontrollable plain orifice valve in the direction from the annularchamber 1166 to the first cylindrical chamber 1160 and may be acontrollable sprung valve in the direction from the first cylindricalchamber 1160 to the annular chamber 1166.

After reaching the annular chamber 1166, the substantiallyincompressible fluid may be permitted to flow without restrictionbetween the annular chamber 1166 and the second cylindrical chamber1162. The fluid may then flow through a second port 1174 into the thirdcylindrical chamber 1164. The second port 1174 may be blocked by a thirdvalve 1176, like the illustrated resilient o-ring, or any otherstructure deemed appropriate by a person having ordinary skill in theart. When the force or pressure of the incompressible fluid in thesecond cylindrical chamber 1162 exceeds the threshold pressure of thethird valve 1176, the substantially incompressible fluid may flowthrough the second port 1174 past or through the third valve 1176 andinto the third cylindrical chamber 1164. This fluid flow from the firstcylindrical chamber 1160, through the first and second valves 1168 and1194, into the annular chamber 1166, into the second cylindrical chamber1162, and into the third cylindrical chamber 1164 may be most likely tooccur during a compression stroke as the piston 1112 moves into andreduces the size of the first cylindrical chamber 1160 andsimultaneously enlarges the third cylindrical chamber 1164. In someembodiments the third valve 1176 may be a weakly sprung valve in thedirection from the second cylindrical chamber 1162 to the thirdcylindrical chamber 1164, and the valve 1176 may substantially preventor block flow from the third cylindrical chamber 1164 to the secondcylindrical chamber 1162.

During the rebound stroke, the substantially incompressible fluid maymove through a third port 1178, which may permit fluid to flow betweenthe third cylindrical chamber 1164 and the annular chamber 1166. Thedamping chamber 1110 may include a fourth valve 1171, which may includea restricting element 1172 and a valve adjuster 1170 that may controlrestriction of fluid flow through the third port 1178. In someembodiments, the restricting element 1172 controlled by the valveadjuster 1170 may be substantially annular and may be positioned withinthe annular chamber 1166. In some embodiments, the restricting element1172 may be a sleeve. In some embodiments, features of the restrictingelement 1172 may extend beyond the exterior surface 1190 of the secondend 1104 and may be manipulable by the user via a knob or otherstructure 1182 to adjust the pressure at which the substantiallyincompressible fluid may flow from the first cylindrical chamber 1160 tothe annular chamber 1166. The rotation of the knob 1182 may rotate theadjuster 1170 to impinge on a tongue 1184 that may extend into theannular chamber 1166. Movement of the tongue 1184 may cause contactbetween the tongue 1184 and one end 1188 of the restricting element1172, thereby moving the restricting element 1172 longitudinally withinthe annular chamber 1166. However, it is often desirable that therestricting element 1172 be permitted to move longitudinally within theannular chamber 1166 other than using the tongue 1184. For example,substantially incompressible fluid moving from the first cylindricalchamber 1160 to the second cylindrical chamber 1162 may impinge on thefirst end 1188 of the restricting element 1172 and thereby may move therestricting element longitudinally towards the second cylindricalchamber 1162. Similarly, fluid flowing from the second cylindricalchamber 1162 to the first cylindrical chamber 1160 may impinge on thesecond end 1190 of the restricting element 1172 and thereby may move therestricting element 1172 longitudinally towards the tongue 1184. Theposition of the restricting element 1172 relative to the third port 1178may affect the fluid flow from the third cylindrical chamber 1164 to theannular chamber 1166 and into the first cylindrical chamber 1160.

The third port 1178 may be positioned so as only to be available forfluid flow for certain positions of the second piston 1112. In manyembodiments, it may be undesirable for fluid in the first cylindricalchamber 1160 to be permitted to flow into the annular chamber 1166through a port other than the first port 1186. Further, in manyembodiments, it may be desirable for substantially incompressible fluidwithin the third cylindrical chamber 1164 to act as a stop and minimizeor prevent the second piston 1112 from “topping out” or reaching thestructure 1192 defining the second port 1174. Accordingly, the thirdport 1178 may be positioned such that it is available for fluid flowonly when it is longitudinally between the second piston 1112 and thesecond port defining structure 1192 or longitudinally between the firstpiston 1108 and the second piston 1112. By so positioning the third port1178, the first piston 1108, the structure 1192 defining the second port1174, and the second piston may remain longitudinally spaced from oneanother during any stroke of the suspension system.

During a compression stroke, the first end 1102 and the second end 1104may telescopically slide towards one another. The first piston 1108 maymove into the gas spring chamber 1106. This motion of the first piston1108 may increase the pressure in the gas spring chamber 1106. Thispressure increase may increase the pressure of the gas in the gas springchamber against the first side 1122 of the floating piston 1120. At thesame time, the second piston 1112 may move into the damping chamber1110. The movement of the second piston 1112 may cause the opening ofthe first valve 1168 as described above to create a damping of themovement of the shock absorber 1100. The movement of the fluid withinthe damping chamber 1110 and its related chambers may be furtheraffected by the pressure applied by the gas in the gas spring chamber1106 to the floating piston 1120. The pressure against, and movement of,the floating piston 1120 may resist movement of the substantiallyincompressible fluid within the damping chamber 1110. Similarly, duringa rebound stroke, pressure may continue to be applied to thesubstantially incompressible fluid in the damping chamber 1110 throughthe force on the gas in the gas spring chamber 1106 and the floatingpiston 1120. The pressure applied by the gas in the gas spring chamber1106 to the floating piston 1120 may minimize or prevent vacuum bubblesfrom forming in the fluid of the damping chamber 1110 in the same way asdescribed for the embodiment of FIG. 10, above. Likewise, varying thegas pressure in the gas chamber 1106 may vary the tension on the seal1118 of the floating piston 1120 that may be overcome in order to allowcompressive movement of the shock absorber 1100, also as described forthe embodiment of FIG. 10. In this manner, gas pressure from the gasspring chamber 1106 may be used to and may affect the damping of theshock movement.

This detailed description in connection with the drawings is intendedprincipally as a description of the presently preferred embodiments ofthe invention, and is not intended to represent the only form in whichthe present invention may be constructed or utilized. The descriptionsets forth the designs, functions, means, and methods of implementingthe invention in connection with the illustrated embodiments. It is tobe understood, however, that the same or equivalent functions andfeatures may be accomplished by different embodiments that are alsointended to be encompassed within the spirit and scope of the inventionand that various modifications may be adopted without departing from theinvention or scope of the following claims.

The invention claimed is:
 1. A shock absorber for a vehicle, comprising:a first end; a second end being configured to telescopically slidinglyinterfit with the first end and at least partially defining a chambercontaining a fluid and comprising at least a first cylindrical chamber,an additional chamber, and an annular chamber; a first port permittingthe fluid to flow between the first cylindrical chamber and the annularchamber; an additional port permitting the fluid to flow between theadditional chamber and the annular chamber; and a valve controllingrestriction of the flow through the additional port, wherein the valvecomprises at least a restricting element and an adjuster.
 2. The shockabsorber according to claim 1, wherein at least a portion of theadjuster extends beyond an exterior surface of the second end.
 3. Theshock absorber according to claim 1, wherein the valve comprises anannular sleeve.
 4. The shock absorber according to claim 3, wherein theannular sleeve is positioned in the annular chamber.
 5. The shockabsorber according to claim 4, wherein the annular sleeve is permittedto move longitudinally within the annular chamber.
 6. The shock absorberaccording to claim 1, further comprising a first piston and a secondpiston longitudinally spaced from one another.
 7. The shock absorberaccording to claim 6, wherein fluid flow through the additional port ispermitted when the additional port is longitudinally between the firstpiston and the second piston.
 8. The shock absorber according to claim1, further comprising a further cylindrical chamber in fluidcommunication with the annular chamber.
 9. The shock absorber accordingto claim 8, further comprising structure defining a further port betweenthe further cylindrical chamber and the additional chamber.
 10. Theshock absorber according to claim 9, wherein fluid flow through theadditional port is permitted when the additional port is longitudinallybetween the first piston and the second piston.
 11. The shock absorberaccording to claim 6, wherein the first piston is positioned within thefirst end.
 12. The shock absorber according to claim 6, wherein thesecond piston is positioned within the second end.
 13. The shockabsorber according to claim 6, further comprising a floating pistonbetween the first piston and the second piston.
 14. The shock absorberaccording to claim 13, wherein the floating piston is a floating barrierthat separates the gas in the gas spring chamber from the substantiallyincompressible fluid in the damping chamber and is configured to move toequalize the pressure between the gas in the first end and thesubstantially incompressible fluid in the second end.
 15. The shockabsorber according to claim 14, wherein the pressure from the gasagainst the floating piston is adequate to minimize cavitation.
 16. Theshock absorber according to claim 14, wherein a gas spring chamber ispositioned within the first end.
 17. The shock absorber according toclaim 14, wherein a damping chamber is positioned within the second end.